Rotary, uni-directional, variable and reversible delivery pump



y 1956 L. M. GARNER ETAL 2,752,851

ROTARY, UNIDIRECTIONAL, VARIABLE AND REVERSIBLE DELIVERY PUMP Filed April 2, 1951 8 Sheets-Sheet 1 I n wanton! LAWRENCE M. GARNER EDWARD 5 ME CONNOHIE By @MWL flKZMMM/L L. M. GARNER ET AL 2 752 851 y 1956 ROTARY, UNI-DIRECTIONAL, VARIABLE AND REVERSIBLE DELIVERY PUMP 8 Sheets-Sheet 2 Filed April 2, 1951 I rwentor:

LAWRENCE M GARNER EDWARD 8 Mc CONNOH/E 0 4 m D w M 7 w 5 'W M \\\\M V 0 M L 0 2 x m l 2 3 y 1956 L. M. GARNER ETAL 2,752,851

ROTARY, UNI-DIRECTIONAL, VARIABLE AND REVERSIBLE DELIVERY PUMP Filed April 2, 1951 8 Sheets-Sheet E Fig. 3. 1/

Fl' .4. 94 76 7' a 92 xmxy '1 50' W57 32/ J s4 44 70 1 2 as 50 68 14 E0 74 as Inventors LAW/FENCE M. GA PNER 52 EDWARD 5. Mc CONNOH/E L. M. GARNER ETAL 2 752 851 July 1956 ROTARY, UNI-DIRECTIONAL, VARIABLE AND REVERSIBLE DELIVERY PUMP Filed April 2, 1951 8 Sheets-Sheet 4 FigQ 6 24 ac b Fig Inventors LAWRENCE M. GARNER ED WARD 5 M9 CONNOH/E B] 6 xf/ w y 1956 L M. GARNER ETAL 2,752,851

ROTARY UNI-DIRECTIONAL, VARIABLE AND REVERSIBLE DELIVERY PUMP Filed April 2, 1951 8 Sheets-Sheet 5 LAWRENCE M. GARNER /5 EDWARD $.Mc CONNOHIE IN VEN TORS E 7% flammi y 1955 L. M. GARNER ETAL 2,752,851

ROTARY, UNI-DIRECTIONAL, VARIABLE AND REVERSIBLE DELIVERY PUMP Filed April 2. 1951 s Sheets-Sheet e Inventors LAWRENCE M GARNER EDWARD 5. M0 CONNOHIE y 1956 L. M. G NER ETAL 2,752,851

ROTARY, UNI-D CTIONAL, VARIABLE AND REVERSIBLE DELIVERY PUMP Filed April 2, 1951 8 sheets-Sheet '7 /7 LAWRENCE M GARNER EDWARD 8. Mc Co/vN OH/E V EN L. M. ARNER EIAL 2,752,851 ROTARY, UN IRECTIO VARIABLE AND R RY PUMP July 11%; 1956 EVERSIBLE DEL 8 Sheets-Sheet 8 Filed April 2, 1951 E 5 mwm M 6 o wm a. m m 0 NW 2 mm c W JN l l .QS W E v. RA B7 MM f LE ROTARY, UNLDIRECUTHONAL, VARIIABLE AND REVERSEBLE DELIVERY PUIVIP Lawrence M. Garner and Edward S. h'letllonnohie, Covert, Mich.

Application April 2, 1951, Serial No. 218,734

11 Qlaims. (Ci. 103--3) This invention, which is a continuation-in-part of the invention in our application Serial No. 776,120, filed September 25, 1947, Patent No. 2,656,796 and entitled A Uui Directional, Rotary Variable Delivery Fluid Pump, relates in general to a uni-directional, rotary pump and more particularly to a type thereof having precisely controllable means for varying and reversing the flow of fluid through said pump.

Rotary pumps having rotors of the general type disclosed in the accompanying drawings are common knowledge as evidenced by the Patent No. 295,704 to J. M. Wiles. However, persons familiar with the construction and operation of pumps of this type have long recognized the need for a compact, rugged means for adjusting the rotor with respect to the center of the pump chamber surrounding same, whereby the direction of fiow and capacity of such pumps can be accurately and easily controlled.

Known attempts to solve this problem have resulted in complicated, unreliable mechanisms necessitating movement of either the pump casing or the rotor shaft; Such movements have been found to limit severely the utility of the pump and positively prevent its adaptation to a variety of installation where variable and reversible fiow pumps can be advantageously used.

For example, a mechanism for varying and reversing the flow through the pump without effecting said undesirable movements of either said casing or rotor shaft will permit the use of such a pump as the driving element of a transmission or power coupling, as will be shown hereinafter, the driven element being substantially conveutional.

Accordingly, a primary object of this invention is the provision of a uni-directional, rotary pump having means whereby the capacity and direction of flow through the pump can be varied without moving either the pump casing or rotor shaft laterally with respect to each other or with respect to means supporting the pump.

A further object of this invention is the provision of a pump, as aforesaid, having means whereby the circumferential wall of the chamber surrounding the pump rotor can be easily and controllably moved diametrically with respect to the rotor shaft for effecting said changes in capacity and direction of flow without etfecting relative movement between the pump casing and rotor shaft.

A further object of this invention is the provision of a uni-directional, rotory pump, as aforesaid, wherein both the capacity and the direction of flow of fluid through the pump may be varied while maintaining the speed and direction of rotation of the pump rotor absolutely constant.

A further object of this invention is the provision of means for controlling the capacity and flow of a rotary pump, as aforesaid, permitting use of said pump in a variety of related applications such, for example, as a power coupler.

Other objects of this invention will become apparent to persons familiar with this type of equipment upon ice reading the following specification and referring to the accompanying drawings in which:

Figure 1 is a perspective view of one embodiment of the pump to which this invention relates.

Figure 2 is a broken, perspective view of the flow control mechanism of said pump removed from its casing.

Figure 3 is a sectional view taken along the vertical and longitudinal center line of the pump casing and rotor.

Figure 4 is a sectional view substantially as taken along the line 44 of Figure 3.

FigureS is a sectional view substantially as taken along the line 5-5 of Figure 3.

Figure 6 is a sectional view substantially as taken along the line 6-6 of Figure 4.

Figure 7 is a sectional view substantially as taken along the line 7-7 of Figure 6.

Figure 8 is a side elevation view of a modification of the pump to which this invention relates.

Figure 9 is an elevation view of one of the head members of the pump casing shown in Figure 1 as viewed from the inside thereof.

Figure 10 is a sectional view taken along the line 10-40 of Figure 9.

Figure 11 is a perspective view of an eccentric bearing in the flow control mechanism.

Figure 12 is a perspective view of the rotor blade in the preferred construction thereof.

Figure 13 is a sectional view substantially as taken along the line l3-13 of Figure 4 with the shaft and rotor removed therefrom.

Figure 14 is a sectional view substantially as taken along the line 14-14 of Figure 13 with the flow control mechanism removed therefrom.

Figure 15 is a sectional view substantially as taken along the line 15-15 of Figure 8.

Figure 16 is a sectional view taken along the line 16-16 of Figure 15.

Figure 17 is a sectional 17-17 of Figure 15.

Figure 18 is a sectional 18--18 of Figure 15.

Figure 19 is a sectional 1919 of Figure 18.

Figure 20 is a sectional Stil-2tl of Figure 18.

Figure 21 is a sectional 21-21 of Figure 18.

General description view taken along the line view taken along the line view taken along the line view taken along the line view taken along the line In meeting those objects heretofore mentioned, as well as others incidental thereto and associated therewith, we have provided a pump casing having a cylindrical control chamber therewithin and a pair of spaced passageways leading from said chamber. Disposed within said chamber and spaced substantially from the circumferential wall thereof is a pump rotor secured upon a shaft rotatably supported in the axial sidewalls of the said chamber. Said rotor is completely surrounded by .a flow control mechanism comprising a plurality of rings and/or disks defining a cylindrical pump chamber snugly adjacent to both axial sides of said rotor and having an inside diam-- eter substantially equal to the tip diameter of the said rotor. The rotor, which is preferably of the general type disclosed in the above mentioned Wiles Patent No. 295,704, has a rim of less diameter than that of the pump chamber, and a plurality of radially movable blades supported upon said rim. By appropriate actuation of said control mechanism the position of the circumferential wall of the pump chamber can be moved diametrically with respect to the rotor shaft and rim, as hereinafter disclosed in detail, for the purpose of varying the capacity and the direction of flow through the said pump.

Detailed description For the purpose of convenience in description, the terms upper, "lower, left and right, as well as derivatives thereof, as used in the following specification, will be understood to have reference to the rotary pump and parts thereof as appearing in Figures 1, 2 and 8. The terms inner and outer, where used, shall have reference to the geometric center of the pump and parts thereof.

As shown in Figures 1, 3 and 14, the uni-directional, rotary pump has a casing 11 comprised of a pair of side plates 12 and 14 clamping therebetween a pair of substantially identical upper and lower head members 15 and 16, respectively (Figures 9 and 10), by means of screws 18, which may be of any conventional type, engaging bores in the head members 15 and 16. Other suitable means, such as bolts extending through appropriate openings in the side plates and head members, may be used to secure the above mentioned members in rigid assembly, if desired. The side plates and head members combine to define a substantially cylindrical control chamber 22 (Figures 4, 6 and 14), for housing the flow control mechanism 21 (Figures 2 and 4).

The side plate 12 is provided with an outwardly extending boss 24 (Figures 1, 4, 5 and 6) having a sidewardiy opening cavity 26 which is covered by the plate 28, removably secured thereto as by screws 30. Generally rectangular end plates 32 (Figures 1, 3 and 13) are detachably secured, as by screws 34, to the leftward and rightward ends of the head members and side plates of the casing 11.

The head members 15 and 16 are provided, in this particular embodiment, with fiuid passageways 38 and 40 which are parallel and open through the rightward end of the casing 11. As Will be shown hereinafter, the flow of fluid through said passageways 38 and 40 may be varied and/or reversed by appropriate manipulation of the flow control mechanism 21. The rightward and leftward ends of upper and lower head members 15 and 16 are spaced from each other (Figures 3, 13 and 14), and with the side plates 12 and 14 define a pair of aligned, horizontal guide passages 42 which communicate with the control chamber at diametrically opposite sides thereof. A pair of preferably identical, rotor control slides 44, substantially rectangular in shape, are slidably disposed within said guide passages 42.

Each head member 15 and 16, is provided with a radially inwardly extending, annular rib 71 (Figures 9, l0, l3 and 14) laterally aligned with, and equal in lateral width to, the slides 44. The rotor 56 is disposed within the control chamber 22 and is substantially spaced both axially and radially from the walls thereof.

The inner surfaces 46 of the slides 44 are arcuately shaped, for purposes appearing hereinafter. The lateral sidewalls of the slides 44 are provided with arcuate ribs 48 adjacent to and concentric with the arcuate surfaces 46. Slides 44 are free to move leftwardly or rightwardly of the pump casing 11 within the limits of the end plates 32.

The side plates 12 and 14 are provided with aligned, centrally disposed shaft openings 50 through which a rotor shaft 52 extends. A rotor 56 (Figures 2, 3 and 4), of the general type shown in the above mentioned Wiles patent, is secured to the shaft 52 by means of a key 54. The rotor 56 is comprised of a hub 55, an annular web 57 and a laterally enlarged annular rim 59, said rim being provided with a plurality, here nine, of radially disposed slots 53 equidistant from each other and extending completely through said rim. The rim 59 is spaced radially inwardly from the ribs 71.

A U-shaped rotor blade 60 (Figure 12), having a notch 66 in the inner edge 62 thereof, thereby providing the leg members 68, is radially disposed within each of said slots 58 so that the web 57 extends into the notch 66 and the leg members 68 extend along either side of the web 57. The inner and outer edges 62 and 64 of the blade 69 are preferably arcuate, as shown in Figure 12, and their surfaces define arcs of a circle having a diameter equal to the length of a blade and having its axis passing through the centerline of said blade. The reason for this limitation, as well as a limitation upon the minimum thickness of the blades will appear hereinafter. The depths of the slots 58 and the notches 66 are such that the outer edge 64 of the blade 60 may be selectively disposed tangentially with the periphery of the rim 5 or extended, as desired, in a conventional manner and for purposes disclosed hereinafter.

The maximum circumferential distance between the centerlines of two adjacent blades is slightly less than the circumferential, or vertical, length of the arcuate surfaces 46 on the slides 44. This prevents by-passing of the fluid between the upper side and lower side of the rotor 56 when it is exterting a pressure upon said fiuid.

A pair of substantially identical, circular rings or open center, side disks 86, having gear teeth 88 on the radially outer edge thereof, are rotatably supported upon the shaft 52, are disposed on opposite sides of the rotor 56 and journaled within the control chamber 22. A pair of substantially identical outer eccentric rings 70 are journaled within the control chamber 22 on opposite sides of the ribs '71 and slides 44 and snugly disposed between the side disks or rings 86 and said ribs 71. The outer peripheries of the rings 70 are provided with teeth 72 preferably having the same pitch and size as the teeth 88 on the side disks 86.

Rotatably journaled within the outer eccentric rings 70 are a pair of inner eccentric rings 74 whose eccentricity is equal to that of the outer rings. The inner circumferences of said inner rings combine to define the circumferential wall of the pump chamber 90, which wall is substantially equal in diameter to the tip diameter of the rotor 56. By appropriate disposition of the inner rings with respect to the outer rings, the axis of the pump chamber can be disposed leftwardly of, rightwardly of, or coincident with the axis of the rotor shaft 52. Such positions are represented by the center-lines aa, bb, and c-c, respectively, in Figure 6. The position b-b may be referred to as the neutral position wherein the rotor rim 59 is co-axial with, and spaced inwardly from the walls of, the pump chamber 90. As shown in Figures 3 and 4, the axis of the pump chamber 90 is in position a-a, leftwardly of the axis of the shaft 52. Thus, fiuid is caused to flow around the leftward end of the rotor 56, when it is rotated.

A pair of circular thrust rings 112 of identical size and shape encircle the hub 55 of the rotor adjacent to the web 57 thereof and engage the inner edges 62 of the blades 60 whereby the outer edges 64 of said blades are held snugly and firmly, but slidably, against the inner walls of the inner eccentric rings 74. The diameter of the rim 59 of the rotor 56 is less than the diameter of the pump chamber 90 by an amount equal to the combined eccentricities of one pair of inner and outer rings. Thus, regardless of the position of the eccentric rings with respect to each other and with respect to the control chamber 22, the blades 60 are held snugly against the inner Walls of the inner rings 74 at all times by the thrust rings 112. The blades 60 are equal in thickness to the combined throw of a pair of inner and outer rings. This construction is necessitated in order that the curved surfaces at the ends of the blades will be in continuous contact with the circumferential wall of the pump chamber 90, regardless of its position with respect to the rim 51.

The inner eccentric rings 74 are provided with circular grooves 76 on their adjacent surfaces, which grooves are concentric with their inner surfaces and slidably receive the above mentioned ribs 48 on the rotor control slides 44. When the ribs 48 are thus associated with the grooves 76, the arcuate' surfaces 46 are concentric and flush with the inner surfaces of the eccentric rings 74.

Each side disk 86 is provided with three or more, here four, circular bearing openings 8d (Figures 2 and 6) preferably, but not necessarily, disposed substantially equidistantly from the center of the side disks 36 and equidistantly from each other. However, as long as the said openings 84 are identically disposed on the two side disks and are alignable with each other they may be placed other than equi-distant from each other equidistant from the center of the side disks. The necessity of having three or more such openings will be discussed hereinafter. A plurality of circular bearings 82 (Figures 2, 6 and 11), each having an eccentric bore 80 therein, are snugly and rotatably disposed one each within each said bearing opening 84.

The inner eccentric rings 74 are provided with stub shafts 78, one for each bearing 82, which shafts are rotatably disposed within the eccentric bores iii? of the bearings 82. The stub shafts 7d are so disposed upon said inner ring 74 that, when said stub shafts are disposed within the bores .80, said bores will be disposed in the same clockwise direction away from the center of their respective bearings 82. Thus, the inner eccentric rings 74, which are rotatable by the disks 86 about the shaft 52, are also movable eccentrically with respect to said disks, such eccentric movement being governed by the eccentricity of the bearing 82 and equal to the eccentricity of either outer ring 70. The stub shafts must also be disposed so that axis of the inner circumference of the outer ring is in the same clockwise direction with respect to the axis of the outer circumference thereof as said clockwise direction of the bores 80 when the inner and outer rings and side ring are assembled. Counterrotation of the side ring and outer ring will effect a rotation of the bearings 82 in the same direction as, and through an are equal to, those of the outer ring.

From the above it will be seen that the rotor 56 is rotatable by the shaft 52 whereas the disks 86 are rotatable with respect to the shaft 52. The inner eccentric rings 74 are supported upon the side disks 86 by means of the stub shafts 78 for rotation therewith. The outer rings '70 are rotatable with respect both to the inner eccentric rings '76 and the side disks 86, and rotate in the same direction as t the bearings 82.

Accordingly, by effecting simultaneous, equal, counterrotation between the side disks 86 and the outer rings '70, by means set forth hereinafter, the eccentricities of the inner and outer rings and the eccentric bearings will cooperate to effect a straight line movement of the pump chamber diametrically of the shaft 52. By appropriate, pre-arrangernent of the inner and outer rings with respect to each other and with respect to the eccentric bearings 82 as described above, said straight line motion is confined to a horizontal plane, or leftwardly and rightwardly as appearing in Figures 2 and 3. The exact position of the center of the pump chamber 9th with respect to the center of the shaft 52, etween the limits of a--a and 12-41 (Figure 6), is controlled by the amount of rotation effected between the side disks 36 and the outer rings 7'0. A 180 rotation of the disks 326, which is accordingly accompanied by a simultaneous 189 rotation of the outer rings 78 in the opposite direction, will move the center of the pump chamber hit from a--a to 12-h. it will be seen that this rotation and the resulting shift or throw in the pump chamber 90 can be accomplished whether the shaft 5'2, and rotor thereon, are rotating or at rest.

The horizontal movement of the pump chamber 90 is accompanied and guided by horizontal movement of the control slides 44- in their respective passages 42 through the interengaging ribs 48 and grooves 76.

For an understanding of the means for adjusting the position of the pump chamber 9i with respect to the rotor 56, attention is directed to Figures 2, 4, 5 and 6. A central shaft 92;, having a worm gear 96 integral therewith and disposed within the chamber 26, is journaled at 94 in the boss 24. The worm gear 96 is engaged with gears 98 and 100 carried on opposite sides thereof by parallel shafts 162 and 104 which are rotatably supported in the side plates 12 and 14 and cover plate 23. These shafts 102 and X04 extend into transfer bores 106 in the head members 15 and 16 (Figures 5 and 13) and are provided with pairs of identical, spaced gears 103 and 110, respectively, for constant meshing with the teeth 88 and 72 of the side disks 86 and outer rings 70, respectively. Accordingly, when the shaft 92 is rotated, by means not shown, gears 103 and 110 are rotated at the same speed in opposite directions, thereby producing the horizontal, straight line shifting of the pump chamber 90, as described above. Obviously, any desired position of adjustment between the limiting positions of aa and b-b may be obtained. The effects of this adjustment are to vary the capacity and delivery of the pump in the following manner.

As shown in Figures 2, 3, 4 and 6, the flow control mechanism 21, controlling the position of the pump chamber 90 with respect to the rim 59, is set so that said pump 90 is at its extreme left hand position. aa, whereby the right side of the rim 59 has zero clearance with the surface 46 of the rightward slide 414 and the adjacent innor surfaces of the inner rings 74. Thus, flow of fluid between the passageways 38 and 40 must proceed around the leftward end of the rotor 56, where maximum clearance between the rim 59 and the adjacent surface 46 of the leftward slide 44 is provided. Consequently, if the rotor 56 is rotated counterclockwise, fluid is carried around the pump chamber 9d by the blades 60 from the passageway 38 and discharged through the passageway to. Obviously, as the chamber 90 is moved rightwardly by appropriate counterrotation of the inner and outer rings, the volume of fluid carried around the left side of therotor 56 is reduced while an increased volume passes around the right side of the rotor 56, thereby decreasing the delivery of fluid through passageway 4t! which, at this instance is the pressure side of the pump. When the center line of the pump chamber 99 reaches position c-c,

where it is coincident with the axis of the shaft 53 (Figure .6), fluid passing around the left side of the rotor 55 will be equal to the fluid passing around the right side of the rotor 56 and the delivery or the pressure of the pump through the passageway 40 will be zero.

As the center line of the chamber 90 is shifted from this neutral position rightwardly toward the limiting position !)b, the volume of fluid passing the rightward side of the rotor will exceed that passing the leftward side, thereby causing the rotor to draw fluid through passageway it and deliver it out of passageway 33, thereby reversing the flow of fluid through the passageways 38 and an.

Thus, it will be seen that with the rotor rotating at a constant speed the delivery of the pump may not only be completely reversed but may also vary from zero to a maximum for either direction of such delivery. Further, it will be seen that the results may be obtained regardless of the direction of the rotation of the rotor and regardless of the speed of its rotation.

it will be observed that the rim 59 of the rotor 56 and the side disks 86 combine with the remainder of the pump chamber 90 to provide an annular chamber through which the fluid must pass at the urging of the blades 64 of the rotor 56. Except for the portions of the pump chamber )0 defined at its outer periphery by the inner surfaces 46 of the slides 44, the rotor 56 is continuously exposed either to the passageway 38 or the passageway 40. Since the vertical dimension of the surface 46 on each slide 44 is greater than the maximum distance between two successive blades of the rotor 56, the slides 4-4 positively prevent pressure leakage between the upper and lower sides of the pump chamber 94], whetherthe rotor is rotating or at rest.

It has been found that Where less than three eccentric bearings 82 are utilized, such as two bearings, there is a tendency for such hearings to counterrotate with respect to each other in certain relative positions of the inner ring 74 and side ring 86, particularly when the pump chamber is in position c-c, thereby locking the ring and disk together. For satisfactory operation the eccentric bearings 82 must always rotate in the same clockwise direction, which may be either clockwise or counterclockwise when adjustments are being made in the position of the pump chamber. With three or more bearings covering an arc in excess of 180 in either direction about the disk 86, at least one hearing will, at all times, be in such position as to prevent such locking by forcing the other two bearings to rotate in the same direction therewith.

it will be seen that, as the pump chamber 90 is shifted from position aa to position c-c, the blades will rock with respect to the circumferential wall thereof. Thus, the curvature of the edges 62 and 64 must be arcs defining a single circle, as defined above, in order to prevent sloppiness or binding in either of said extreme positions. Likewise, the thickness of the blades 60 must be at least equal to the combined throw of the inner and outer rings to ensure continuous contact between the arcuate edges of the blades and the circumferential wall of the pump chamber and thrust rings 112 during said rocking of the blades.

Modified structure The modification of my invention shown in Figures 8, 15, 16 and 17, discloses a hydraulic coupling 115 comprising a driving section 116 and a driven section 117 (Figures 8 and 15).

The driving section 116 is, for all practical purposes, substantially equivalent to the uni-directional,rotary pump 10, described and disclosed hereinabove. The driving section 116 is comprised of a casing 118 having a removable side plate 119 secured thereto by any convenient, conventional means. A cylindrical control chamber 121 is provided within the casing 118, and the side plate 119 is provided with a cylindrical boss 122 co-axial with, and of substantially less diameter than, the control chamber 121 and extending axially thereinto. A pair of axially aligned shaft openings 123 and 124 are provided in the side plate 119 and sidewall of the casing 118 (Figure 15) co-axial with the control chamber 121. A drive shaft 125, which is journaled in the shaft opening 123 in the side plate 119 and extends partially into the shaft opening 124 in the sidewall 120, has a rotor 126 mounted thereon within the control chamber 121 and is so disposed snugly but slidably between the adjacent surfaces of the sidewall 120 and cylindrical boss 122. The rotor 126 may be substantially identical to the rotor 56, discussed and described hereinabove. The tip circumference of the rotor 126, including the blades 12? thereon, has a maximum radius substan tially smaller than the radius of the cylindrical boss 122, for reasons appearing hereinafter.

A side ring 128 having gear teeth 129 on its outer periphery is snugly but rotatably journaled upon the cylindrical boss 122 with the control chamber 121 with its one side flush with the boss 122. An outer eccentric ring 131, whose axial width is substantially equal to that of the rotor 126, is journaled within the control chamber 121 between the side ring 128 and the adjacent sidewall 120 of the pump casing 118. The outer ring 121 is provided with teeth 132 on its outer periphery having the same pitch and size as the gear teeth 129 on the side ring 128..

An inner eccentric ring 133 is rotatably journaled snugly within the outer ring 121 and is substantially equal in axial width thereto. The eccentricities of the inner and outer rings are equal. As was the case in the control mechanism 21 of the pump 10, the combined eccentricities of the inner and outer rings 131 and 133 are equal to the maximum eccentricity of the said tip circumference of the rotor 126.

Three circular bearing openings 134 (Figure 16) are provided in the side ring 128 preferably, but not necessarily, equi-distant from the center thereof and spaced equi-distantly from each other. An eccentric bearing 135, substantially identical to the bearing 82 in the pump 10, is disposed within each one of the bearing openings 134. Stub shafts 136 extend axially from, and are integral with, the same side of the inner ring 133 for reception into the eccentric bores 137 in the bearing 135. As.

was the case in the control mechanism 21 of the pump 10, the eccentric bores 137 of the bearings are disposed in identical clockwise directions with respect to the centers of their respective bearings when the stub shafts 136 are rotatably disposed within the eccentric bores 137. Thus, an eccentric motion of limited extent is permitted between the inner ring 133 and the side ring 128 while the inner ring is rotated therewith about the shaft 125. Likewise, the eccentricity of the outer ring is in the same direction as the eccentricity of said bearings when the flow mechanism is assembled.

The diameter of the inner wall of the inner ring 133, which is substantially identical to the tip diameter of the rotor 126 is substantially smaller than the diameter of the cylindrical boss 122 so that regardless of the position of the inner ring 133, the pump chamber 138 will always be defined by the inner surface of the inner ring 133 and the adjacent surfaces of the boss 122 and sidewall 120 of the pump casing 118. The purpose of this structure is to prevent the excessive pressure created in the pump chamber from being exerted upon the side ring 128 and thereby binding it against the side plate 119. Such structure also prevents the imposition of excessive pressures upon the eccentric bearings 135.

A pair of diametrically disposed, arcuate slots 141 and 1142 (Figures 18, 19, 20 and 21), which are substantially co-axial with the drive shaft 1.25, are provided in the easing sidewall 129. Although the slots may have a variety of shapes and contours within the scope of this invention, said slots are herein shown as having varying radial widths between the ends thereof. The corresponding leftward and rightward ends of the slots 141 and 142 are separated by lands 143 and 144. The slots 141 and 142, as shown in Figures 21 and 20, are gradually reduced about 50% in their radial width from the leftward ends thereof to their midpoints. Then, that side of each slot adjacent to the side plate 119 gradually increases toward its rightward end to the radial width of the leftward end when it reaches the land 1%. However, that lateral side of each slot remote from said side plate 119 continues to reduce from the midpoint thereof, as shown in Figure 21, down to a very small crack where it joins the land 114 at the rightward end thereof. The reasons for this will become apparent hereinafter.

The driven section 1.17 is comprised of a substantially cylindrical casing 145 having a shaft opening 146 through the side wall 147 thereof co-axial with the housing 145. The housing 145 is secured by any convenient, conventional means to the casing side wall 120 so that the shaft opening 146 is co-axial with the shaft opening 124. The housing 145 is provided with an eccentric chamber 143 with a rotor 149 which may, for practical purposes, be substantially identical to the rotor 126. The rotor 149 is mounted upon and rotatable with a driven shaft 151 journaled in the shaft opening 146 and extending into the shaft opening 144 abutting the drive shaft 145. The axis of the eccentric chamber 148 is in this embodiment always leftwardly (Figure 15) of the axis of the driven shaft 151.

avsasst ward to the rightward ends thereof (Figure 18). This arrangement is preferable since it adequately provides for the passage of fluid through the slots into the eccentric chamber 148. The leftward portion of the outer radial edge of each arcuate slot adjacent to the rotor 126 is aligned with the circumferential wall of the pump chamher 138 when in its extreme leftward position. The rightward portion of the outer radial edge of each slot adjacent to the rotor 126 is aligned with said wall of the pump chamber when in its extreme rightward position. These two portions are connected by a short edge portion parallel with the horizontal line between the two extreme positions.

The inner radial edges of the slots, adjacent to said rotor 126, are aligned with the circumference of the rim of the rotor 126. Thus, regardless of the position of the pump chamber with respect to the rotor 126, fluid can flow unobstructedly through the slots 141 and 142 between the pump chamber 138 and the eccentric, chamber 148.

In the modification disclosed by the hydraulic coupling 115, the arcuate slots 141 and 142 replace the passageways 38 and 40 of the pump 10. Thus, depending upon the position of the pump chamber 138 with respect to the rotor 126 and the direction of rotation, fluid can be urged to flow by rotation of the rotor 126 through the slots 141 and 142 in opposite directions between the eccentric chamber 148 and the pump chamber 138. If fluid is caused by the rotor 126 to flow through the slot 141 into the eccentric chamber 148, as shown in Figure 18, the driven rotor 149 will rotate in a counterclockwise direction, and, if the fluid is caused to flow through the slot 142 from the pump chamber 138 to the eccentric chamber 148, the rotor 149 will rotate in a clockwise direction. However, if the rim of the rotor 126 is co-axial with the pump chamber 138, which is neutral position, fluid is simply revolved by the rotor 126 and flows in neither direction through said slots. Thus, since rotor 149 cannot rotate unless fluid is flowing through said slots, placing the pump chamber 138 in neutral position tends to block rotation of the rotor 149. The utility of this feature in a hydraulic transmission is obvious.

The operation of the eccentric rings 131 and 133 in combination with the eccentric bearings 135 in the side ring 123 which eifects a straight line movement of the pump chamber 133 diametrically of the drive rotor 126, is substantially identical to the operation between the eccentric rings 70 and 74 and the bearings 82 in the side disks 86 effecting the same motion between the pump chamber 911 and the shaft 52, as discussed and described in detail hereinabove with respect to the pump 10.

The circumferential, vertical lengths of the lands 143 and 144 adjacent to the pump chamber 138 are greater than the maximum center line distance between two adjacent rotor blades 127 to prevent pressure leaks around the rotor 126, as discussed with reference to the pump 11?. Thus, the lands 143 and 144 take the place of the control slides 44 in the pump 10. It will be recognized that although the driven rotor 149 is herein disclosed and described as substantially identical to the drive rotor 126, such is not necessary within the concept of this invention. Likewise, the rotors 126 and 56 may be varied within this invention.

The teeth 129 on the side ring 128 (Figure 16) are engageable by a pinion 152 housed in the casing 118 and secured on a shaft 153 extending through the side plate 119. The teeth 132 on the outer eccentric ring 131 (Figures 15 and 17) are engageable by'a pinion 154 housed in the casing 118 and secured on a shaft 155 extending through the side plate 119 and parallel with the shaft 153. The pinions 152 and 154 are preferably identical in pitch and size. A pair of interengaging, preferably identical gears 156 and 157 are secured to the shafts 153 and 155, respectively, externally of the side plate 119. Thus, simultaneous, equal, counteirm tation between the side plate 128 and outer ring 131, hence between said inner and outer eccentric rings, can be accomplished simply by rotating either or both of said gears 156 and 157. Control of such rotation will control the direction of flow and volume of fluid passing through the slots 141 and 142.

Although the above mentioned drawings and description apply to one particular, preferred embodiment of the invention, it is not my intention, implied or otherwise, to eliminate other variations or modifications which do not depart from the scope of the invention unless specifically stated to the contrary in the hereinafter appended claims.

We claim:

1. In a uni-directional, rotary pump having a casing with a cylindrical control chamber therein and a rotor disposed within said chamber, spaced from the circumferential wall thereof and mounted for rotation by a shaft co-axial with said chamber, the improvement in means defining, and controlling the eccentricity of, the circumferential wall of a pump chamber surrounding said rotor comprising: an outer ring journaled within said control chamber the bore of said ring being eccentric to the periphery thereof; an inner ring journaled in the bore of said outer ring, the bore of said inner ring being eccentric with the pe iphery thereof by an amount equal to the eccentricity of said outer ring bore, said inner ring bore providing the circumferential wall of said pump chamber; a circular side member journalled concentrically within said control chamber adjacent said inner ring, said inner ring being rotatable with and by said side member; and means engageable with the periphery of said outer ring and side member for producing equal, simultaneous counterrotation of said side member and said outer ring thereby effecting a straightline movement of said pump chamber diametrically of said shaft.

2. In a uni-directional, rotary pump having a casing with a cylindrical control chamber therein and a rotor disposed within said chamber, spaced from the circumferential wall thereof and mounted for rotation by a shaft co-axial with said chamber, the improvement in means defining, and controlling the eccentricity of, the circumferential wall of a pump chamber surrounding said rotor comprising: a circular side member journaled concentrically in said control chamber; an outer ring journaled within, and upon the circumferential wall of, said control chamber adjacent to said side member, the bore of said outer ring being eccentric to the periphery thereof, said member and outer ring being substantially equal in diameter; an inner ring journaled within the bore of said outer ring, the bore of said inner ring being eccentric to the periphery thereof by an amount equal to the eccentricity of said outer ring, said inner ring bore providing the circumferential wall of said pump chamber; means connecting said inner ring to said side member for inducing rotation of said inner ring, when said member is rotated, in the same direction and amount; and means engaging the peripheries of said member and outer ring for producing equal, simul taneous, counterrotation of said side member and said outer ring thereby effecting a straightline movement of said pump chamber diametrically of said shaft.

3. In a unidirectional, rotary pump having a casing with a cylindrical control chamber therein and a rotor disposed within said chamber, spaced from the circumferential Wall thereof and mounted for rotation by a shaft coaxial with said chamber, the improvement in means defining, and controlling the eccentricity of, the

circumferential wall of a pump chamber surrounding said rotor comprising: an outer ring journaled within, and upon the circumferential wall of, said control char her, the bore of said ring being eccentric to the periphery thereof; an inner ring journaled within the bore of said outer ring, the bore of said inner ring being eccentric to the periphery thereof by an amount equal to the eccentricity of the bore of said outer ring, said inner'ring bore providing the circumferential wall of said pump chamber; a circular side member journaled concentrically within said control chamber adjacent to said inner and outer rings, said inner ring being rotatable with said side member; and means engageable with the peripheries of said outer ring and said side member for effecting equal, simultaneous counterrotation of said side member and said outer ring, thereby producing a straightline movement of said pump chamber diametrically of said shaft.

4. In a uni-directional, rotary pump having a casing with a cylindrical control chamber therein and a rotor disposed within said chamber, spaced from the circurnferential wall thereof and mounted for rotation by a shaft co-axial with said chamber, the improvement in means defining, and controlling the eccentricity of, the circumferential wall of a pump chamber surrounding said rotor comprising: an outer ring journaled within, and upon the circumferential wall of, said control chamber, the bore of said ring being eccentric to the periphery thereof and said periphery having gear teeth; an inner ring jouinaled within the bore of said outer ring, the bore of said inner ring being eccentric to the periphery thereof by an amount equal to the eccentricity of said outer ring bore, said inner ring bore providing the circumferential wall of said pump chamber; a circular side member journalcd concentrically within said control chamber adjacent to said inner and outer rings, said member having gear teeth on its periphery and said inner ring being rotatable with said member; geared means engaging the gear teeth of said member and outer ring and means causing said geared means to effect equal, simultaneous counterrotation of said side member and said outer ring, thereby producing a straight-line movement of said pump chamber diametrically of said shaft.

5. in a uni-directional, rotary pump having a casing with a cylindrical control chamber therein and a rotor mounted for rotation Within said chamber by a shaft coaxial therewith, said rotor being spaced from the circumferential wall of said chamber, the improvement in means defining, and controlling the eccentricity of, the radial wall of a pump chamber surrounding said rotor comprising: a circular side member journaled concentrically in said control chan'iber, said member having at least three cylindrical openings therethrough whose axes are parallel with and'equidistant from the axis of said mem ber; a bearing journaled within each of said openings, said bearings having bores equally eccentric to their respective peripheries; an outer ring journaled within, and upon the circumferential wall of, said control chamber, the bore of said ring being eccentric to the periphery thereof by an amount equal to the eccentricity of said bearing bores; an inner ring journaled within the bore of said outer ring and adjacent to said side member, the bore of said inner ring being eccentric to the periphery thereof by an amount equal to the eccentricity of the bore of said outer ring, and said inner ring bore providing the radial wall of said pump chamber; a plurality of stub shafts, equal in number to said bearings, secured to and extending from said inner ring into said bearing bores, the axes of said stub shafts being parallel with and equidistant from the axis of the periphery of said inner ring; and means engagable with the peripheries of said outer ring and said side member for effecting equal, simultaneous counterrotation of said member and outer ring.

6. The construction of claim in which said rotor has a rim of less diameter than said pump chamber, said rim having a plurality of equally spaced, radially dispose slots; a plurality of blades having arcuate inner and outer edges, one blade being slidably disposed in each slot; and a blade ring encircling said shaft, the

periphery of said blade ring engaging the inner edges of saidrblades and holding the outer'edges thereof snugly against said inner ring.

7. The construction of claim 5 in which said rotor has a rim of less diameter than said pump chamber, said rim having a plurality of equally spaced, radially disposed slots; a plurality of blades having arcuate inner and outer edges, one blade being slidably disposed in each slot; a blade ring encircling said shaft, the periphery ofsaid blade ring engaging the inner edges of said blades and firmly holding the outer edges thereof against said inner ring; and means defining a pair of passageways in that side wall of said casing remote from said side member and communicating with said pump chamber near its periphery on opposite sides of a diameter thereof, said passageways being spaced from each other a distance greater than the circumferential distance between two said slots.

8. The construction of claim 5 in which said rotor has a rim of less diameter than said pump chamber, said rim having a plurality of equaly spaced, radially disposed slots; a plurality of blades having arcuate inner and outer edges, one-blade being slidably disposed in each slot, said arcuate edges comprising segments of a cylinder whose diameter is equal to the radial length of each blade, the axis of said cylinder passing substantialy through the center of said blade; a blade ring encircling said shaft, the periphery of said blade ring engaging the inner edges of said blades and firmly holding the outer edges thereof against said inner ring; and means defining a pair of passagesways in that side wall of said casing remote from said side member and communicating with said pump chamber near its periphery on opposite sides of a diameter thereof, said passageways being spaced from each other a distance greater than he circumferential distance between two said slots.

9. The construction of claim 5 in which said rotor has a rim of less diameter than said pump chamber, said rim having a plurality of equally spaced, radially disposed slots; a plurality of blades having arcuate inner and outer edges, one blade being slidably disposed in each slot; a blade ring encircling said shaft, the periphery of said blade ring engaging the inner edges of said blades and firmly holding the outer edges thereof against said inner ring, each blade being radially extendable from said rim by said blade ring a distance equal to the combined eccentricity of said inner and outer rings; and means defining a pair of passageways in the side wall of said casing communicating with said pump chamber near its periphery on opposite sides of a diameter thereof, said passageways being spaced from each other a distance greater than the circumferential distance between two said slots.

10. The construction of claim 5 in which said rotor has a rim of less diameter than said pump chamber, said rim having a plurality of equally spaced, radially disposed slots; a plurality of blades having arcuate inner and outer edges, one blade being slidably disposed in each slot, said arcuate edges comprising'segments of a cylinder whose diameter is equal to the radial length of each blade, the axis of said cylinder passing substantially through the center of said blade; a blade ring encircling said shaft, the periphery of said blade ring engaging the inner edges of said blades and firmly holding the outer edges thereof against said inner ring, each blade being radially extendable from said rim by said blade ring a distance equal to the combined eccentricity of said inner and outer rings; and means defining a pair of passageways in the side wall of said casing communicating with said pump chamber near its periphery on opposite sides of a diameter thereof, said passageways being spaced from each other a distance greater than the circumferential distance between two said slots.

11. In a uni-directional, rotary pump having a casing with a cylindrical control chamber therein and a rotor -;mounted for rotation within said chamber by a shaft co- I 13 axial therewith, said rotor being spaced from the circumferential wall of said chamber, the improvement in means defining, and controlling the eccentricity of, the radial Wall of a pump chamber surrounding said rotor comprising: a circular side member journaled concentrically in said control chamber, said member having at least three cylindrical openings therethrough whose axes are parallel With and equidistant from the axis of said member; a bearing journaled within each of said openings, said bearings having bores equally eccentric to their respective peripheries; an outer ring journaled Within, and upon the circumferential Wall of, said control chamber, the bore of said ring being eccentric to the periphery thereof by an amount equal to the eccentricity of said bearing bores; an inner ring journaled within the bore of said outer ring and adjacent to said side member, the bore of said inner ring being eccentric to the periphery thereof by an amount equal to the eccentricity of the bore of said outer ring, and said inner ring bore providing the radial wall of said pump chamber; a plurality of stub shafts, equal in number to said bearings, secured to and extending from said inner ring into said bearing bores, the axes of said stub shafts being parallel with and equidistant from the axis of the periphery of said inner ring; and means engagable with the peripheries of said outer ring and said side member for effecting equal, simultaneous counterrotation of said member and outer ring and, thereby, a straight-line movement of said pump chamber diametrically of said shaft.

References Cited in the file of this patent UNITED STATES PATENTS Germany May 22, 1933 

